CN105667294A - Transmission device for front-drive plug-in hybrid vehicle - Google Patents
Transmission device for front-drive plug-in hybrid vehicle Download PDFInfo
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- CN105667294A CN105667294A CN201610121126.3A CN201610121126A CN105667294A CN 105667294 A CN105667294 A CN 105667294A CN 201610121126 A CN201610121126 A CN 201610121126A CN 105667294 A CN105667294 A CN 105667294A
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
- B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
- Hybrid Electric Vehicles (AREA)
Abstract
The invention provides a transmission device for a front-drive plug-in hybrid vehicle. The transmission device for the front-drive plug-in hybrid vehicle comprises a small motor (EM1), a big motor (EM2), a planetary gear power coupling mechanism and a double reduction gear train and is provided with a first brake (B1), a second brake (B2), a first clutch (C0), a second clutch (C1) and a third clutch (C2) to realize a plurality of pure electric driving modes and a hybrid driving modes, wherein the planetary gear power coupling mechanism consists of two single planetary gear rows. During pure electric driving, the clutch C0 is opened to be separated from an engine and the brake B1 and the brake B2 are controlled to be closed or opened to realize the pure electric driving mode with three gears. When the clutch C0 is closed, the engine participates in working to enter the hybrid driving mode, and B1, B2, C1 and C2 are controlled in a coordinated way to realize a hybrid driving mode with a plurality of fixed rotation ratios and a power shunting driving mode with a plurality of fixed rotation ratios. The invention has the advantages of high transmission efficiency, high torque output performance and the like and is suitable for power coupling and transmission of the plug-in hybrid vehicle.
Description
Technical field
The present invention relates to a kind of automobile transmission mechanism, in particular to a kind of transmission mechanism for forerunner's plug-in hybrid vehicle.
Background technology
In order to tackle the problem such as energy security, topsoil, Ge great motor corporation is all actively taking counter-measure, mainly concentrates on improvement, the exploitation of new forms of energy drive system of internal-combustion engine system. Compare ripe hybrid power system and the plug-in hybrid power system developed on this basis technically, all become the possible technique scheme that present stage solves automobile energy consumption and environmental pollution, and there are wide market outlook.
The hybrid power system produced in enormous quantities at present all belongs to deep hybrid power system, and representative product is first single planetary row hybrid electric vehicle PRIUS that company of Toyota releases for 1997. This vehicle adopts sun and planet gear mechanism as dynamic coupling device, and compact construction, to take space little, is more satisfactory hybrid power scheme. But for more stressing the plug-in hybrid power system of pure motor driving, also there is certain deficiency in the program. The moment of torsion of such as engine needs namely to increase, by the little motor balance being connected with sun gear, the torque demand that engine just needs to improve little motor, and the constructional feature of this system limits its matching capacity. When pure motor driving, this system can only realize the electric-only mode of single gear, cannot be optimized by electric machine operation state. Therefore Toyota's system is when for plug-in hybrid power system, also has room for promotion significantly.
Summary of the invention
Efficient driving and the transmission mechanism for forerunner's plug-in hybrid vehicle of high pulling torque output can be realized it is desirable to provide a kind of.
The present invention is realized by following scheme:
For a transmission mechanism for forerunner's plug-in hybrid vehicle, comprise little motor EM1, heavy motor EM2, first clutch coupling C0, differential mechanism, input shaft, output shaft, also comprises the first single planetary row PG1, 2nd single planetary row PG2, first stopper B1, 2nd stopper B2, first step down gear Z1, 2nd step down gear Z2, 3rd step down gear Z3, described first single planetary row comprises the first sun gear S1, the first row star-wheel P1, the first row carrier PC1 and the first external toothing R1, described 2nd single planetary row PG2 comprises the 2nd sun gear S2, 2nd satellite gear P2, 2nd planet carrier PC2 and the 2nd external toothing R2, described first single planetary row PG1 and the 2nd single planetary row PG2 formation sun and planet gear power coupling mechanism placed side by side, the first row carrier PC1 of described first single planetary row and the 2nd external toothing R2 of described 2nd single planetary row is connected to form the first axle, first external toothing R1 of described first single planetary row and the 2nd planet carrier PC2 of described 2nd single planetary row is connected to form the 2nd axle, 2nd axle installs the first step down gear Z1,2nd step down gear Z2 is connected by the first rotating shaft with the 3rd step down gear Z3, described first step down gear Z1 is meshed with the 2nd step down gear Z2 and forms first step reduction gear train, and described 3rd step down gear Z3 is meshed with the 4th step down gear Z4 being arranged on differential casing and forms second stage reduction gear train,Described differential mechanism connects output shaft; First sun gear S1 of described first single planetary row is connected with the rotor spindle of described little motor EM1, and the rotor spindle of the 2nd sun gear S2 and described heavy motor EM2 of described 2nd single planetary row is connected; One end of first stopper B1 is fixed on wheel box housing, its the other end is by the 2nd rotating shaft and the first clutch coupling C0's while be connected, the other side of the first clutch coupling C0 is connected on input shaft, and input shaft is connected with the output shaft of engine by flywheel vibroshock FW; Described 2nd stopper B2 one end is fixed on wheel box housing, and its other end is connected with the rotor spindle of little motor EM1.
Exporting for better obtaining high pulling torque, also comprise the 2nd clutch coupling C1, the rotor spindle with heavy motor EM2 of described 2nd clutch coupling C1 is connected, and its other side is connected with input shaft.
Further, also comprising the 3rd clutch coupling C2, described 3rd clutch coupling C2 is claw-type structure, and described 3rd clutch coupling C2 is connected with the rotor spindle of described little motor EM1, the 2nd rotating shaft, the first axle respectively. Under the 3rd clutch coupling C2 not actuator state, the 2nd rotating shaft and the first axle are linked together by claw-type structure; Under the 3rd clutch coupling C2 actuator state, claw-type structure will connect the rotor spindle of the 2nd rotating shaft and little motor EM1. When the 3rd clutch coupling C2 start, closed first clutch coupling C0 and the first stopper B1, engine is connected by the rotor spindle of little motor EM1 with sun and planet gear coupling mechanism, it is achieved the hybrid power reversing mode of vehicle.
Further, when the engine assembly mated mutually with performance, described engine, little motor, sun and planet gear power coupling mechanism, heavy motor be arranged in co-axial alignment placement successively, and the Power output of sun and planet gear power mechanism is arranged between little motor and heavy motor, the Power output of sun and planet gear power mechanism is passed to output shaft by reduction gear train through differential mechanism. Wherein the moment of torsion rotating speed of engine to be mated mutually with the rotating speed moment of torsion of heavy motor, little motor, and whole system performance just can be made optimum.
Plug-in hybrid system emphasizes the ability of pure motor driving more, and the first clutch coupling C0, the 2nd clutch coupling C1 are designed to often open type, just disconnect with engine by default.
According to prior art it will be seen that single planetary row generally all comprises sun gear, satellite gear, planet carrier and external toothing, satellite gear is arranged on planet carrier, and satellite gear is meshed with sun gear and external toothing respectively. Specifically in the present invention, in the first single planetary row PG1, connection between each parts is closed and is: the first row star-wheel P1 is arranged on the first row carrier PC1, and the first row star-wheel P1 respectively with the first sun gear S1 and the first external toothing R1 is meshed; In 2nd single planetary row PG2, connection between each parts is closed and is: the 2nd satellite gear P2 is arranged on the 2nd planet carrier PC2, and the 2nd satellite gear P2 the respectively with two sun gear S2 and the 2nd external toothing R2 is meshed.
A kind of transmission mechanism for forerunner's plug-in hybrid vehicle of the present invention, its power is passed to wheel by differential mechanism thus drives vehicle movement. First clutch coupling C0 is set between input shaft and the 2nd rotating shaft, between input shaft and the rotor spindle of heavy motor EM2, is provided with the 2nd clutch coupling C1. Under hybrid mode, to realize engine coaxial with heavy motor EM2 for closed 2nd clutch coupling C1, and transmission mechanism will with fixed drive ratio paralleling model output high pulling torque. 2nd rotating shaft arranges the first stopper B1, the rotor spindle of little motor EM1 is provided with the 2nd stopper B2.When hybrid mode, closed 2nd stopper B2 can lock only little motor EM1, it is to increase the transmission efficiency of transmission mechanism.
A kind of transmission mechanism for forerunner's plug-in hybrid vehicle of the present invention, little motor EM1 in the bi-motor adopted mainly plays the function of generating effect and starting engine, and heavy motor EM2 mainly plays driving effect, the dynamic coupling device adopted is by the first single planetary row and the 2nd single planetary row sun and planet gear power coupling mechanism formed placed side by side, transmitting ratio between first single planetary row and the 2nd single planetary row arranges and is not restricted each other, structure design is more flexible, and the structure of single planetary row is simply more conducive to reducing gear transmission noises simultaneously. The present invention, by the accurate control to little motor EM1 and heavy motor EM2, makes engine be in the working order of high-level efficiency and low emission all the time.
A kind of transmission mechanism for forerunner's plug-in electric vehicle of the present invention, the first stopper B1, the 2nd stopper B2, the first clutch coupling C0, the 2nd clutch coupling C1 are common multi-sheet wet-type shifting element, and the 3rd clutch coupling C2 adopts claw-type structure clutch coupling. In most of the cases, the 3rd clutch coupling C2 is in not under actuator state, connects the 2nd rotating shaft and the first axle, owing to adopting pawl shape mode of connection, avoids hydraulic efficiency system to continue to provide high-pressure oil, reduces energy expenditure.
When automobile travels with electric-only mode, the first clutch coupling C0 and the 2nd clutch coupling C1 opens simultaneously and is departed from by engine, closed first stopper B1, adopts motor EM1 and motor EM2 to drive simultaneously and can realize the first gear fixed drive ratio driving; Closed 2nd stopper B2, adopts separately motor EM2 to drive and realizes the fixed drive ratio driving of second gear position. When the first stopper B1 and the 2nd stopper B2 opens, by the stepless change under the rotating speed control realization automobile electric-only mode of heavy motor, little motor, being namely defined as the pure electric Drive Mode in third gear position.
When automobile travels with hybrid power economic model, first clutch coupling C0 closes, engine participation work, vehicle travels with dynamic branch pattern, now engine part power is passed to output shaft gear by mechanical transmission, part power is passed to output shaft gear by electrical power path, it is achieved to Continuous optimization and the stepless shift function of engine operation state, i.e. E-CVT function. When the speed of a motor vehicle is higher, little motor EM1 needs to control to regulate the working order of engine near zero rotating speed, and now little motor EM1 efficiency is very low. Little motor EM1 is only locked by the 2nd stopper B2 that is located on little motor EM1 axle by the present invention, avoid little motor EM1 and it is operated in inefficient interval, it is to increase the transmission efficiency of transmission mechanism.
When automobile travels with hybrid power motion pattern, whole car needs high pulling torque to export to meet dynamic property requirement, now can drive pattern by cooperation control first stopper B1, the 2nd stopper B2, the first clutch coupling C0 and the 2nd clutch coupling C1 hybrid power that realizes multiple fixed drive ratio. Closed stopper B1 and clutch coupling C1 simultaneously, engine and heavy motor EM2, by coaxial transmission, are that the first gear hybrid power drives pattern, only adopt engine and heavy motor EM2 to drive and just can obtain enough driving moments of torsion.
The speed of a motor vehicle is higher need high pulling torque to export time, operating mode of such as overtaking other vehicles at a high speed, now closed 2nd stopper B2 and the 2nd clutch coupling C1.
When the first clutch coupling C0 and the 2nd clutch coupling C1 is simultaneously closed, the same rotational speed of all elements of sun and planet gear power coupling mechanism, machinery driving efficiency reaches the highest, it is achieved directly gear drives.
When moveing backward, preferentially use electric-only mode, closed first stopper B1, drive simultaneously realize reverse travel by heavy motor EM2 or little motor EM1 or heavy motor, little motor. When battery electricity is not enough, the 2nd clutch coupling C2 start, engine is connected on little motor EM1 rotor spindle by closed clutch coupling C0 simultaneously, it is achieved hybrid power reversing mode.
A kind of transmission mechanism for forerunner's plug-in hybrid vehicle of the present invention, compared with prior art, has the following advantages:
1. realize the pure electric Drive Mode of three gears, both can meet the speed of a motor vehicle requirement of pure motorized motions, it is also possible to meet the dynamic property demand of pure motor driving; Adopt heavy motor, little motor two motors machine operation point can be optimized control when driving, it is to increase power system efficiency simultaneously.
2. adopt dynamic branch to drive pattern as the main operation modes of mixed dynamic state, it is possible to ensure the fuel economy that whole car is good; Design multiple fixed drive ratio pattern simultaneously, meet dynamic property drive demand better. The all right modular design of each stopper, clutch coupling, matches according to product orientation, conveniently realizes tandem product exploitation.
Accompanying drawing explanation
Fig. 1: for the one-piece construction schematic diagram of the transmission mechanism of forerunner's plug-in electric vehicle
The equivalent lever figure of the Fig. 2 (a): the first pure electric Drive Mode of gear
Fig. 2 (b): the equivalent lever figure of the pure electric Drive Mode in second gear position
Fig. 2 (c): the equivalent lever figure of the pure electric Drive Mode in third gear position
Fig. 3 (a): the first gear hybrid power drives the equivalent lever figure of pattern
Fig. 3 (b): second gear position hybrid power drives the equivalent lever figure of pattern
Fig. 3 (c): third gear position hybrid power drives the equivalent lever figure of pattern
Fig. 3 (d): fourth gear position hybrid power drives the equivalent lever figure of pattern
Fig. 3 (e): fifth gear position hybrid power drives the equivalent lever figure of pattern
Fig. 4: the equivalent lever figure of hybrid power reversing mode
Embodiment
Below in conjunction with embodiment, the invention will be further described, but the present invention is not limited to the statement of embodiment.
Embodiment 1
A kind of transmission mechanism for forerunner's plug-in hybrid vehicle, as shown in Figure 1, comprising little motor EM1, heavy motor EM2, the first clutch coupling C0, the 2nd clutch coupling C1, the 3rd clutch coupling C2, differential mechanism 1, input shaft 2, output shaft 3, first single planetary row PG1, the 2nd single planetary row PG2, the first stopper B1, the 2nd stopper B2, the first step down gear Z1, the 2nd step down gear Z2, the 3rd step down gear Z3, the first clutch coupling C0, the first clutch coupling C1 in the present embodiment is for often driving type clutch coupling, first single planetary row PG1 comprises the first sun gear S1, the first row star-wheel P1, the first row carrier PC1 and the first external toothing R1, the first row star-wheel P1 is arranged on the first row carrier PC1, and the first row star-wheel P1 respectively with the first sun gear S1 and the first external toothing R1 is meshed, 2nd single planetary row PG2 comprises the 2nd sun gear S2, the 2nd satellite gear P2, the 2nd planet carrier PC2 and the 2nd external toothing R2,2nd satellite gear P2 is arranged on the 2nd planet carrier PC2, and the 2nd satellite gear P2 the respectively with two sun gear S2 and the 2nd external toothing R2 is meshed, first single planetary row PG1 and the 2nd single planetary row PG2 formation sun and planet gear power coupling mechanism 4 placed side by side, the 2nd external toothing R2 of the first row carrier PC1 and the 2nd single planetary row PG2 of the first single planetary row PG1 is connected to form the first axle 5, the 2nd planet carrier PC2 of the first external toothing R1 and the 2nd single planetary row PG2 of the first single planetary row PG1 is connected to form the 2nd axle 6, 2nd axle 6 installs the first step down gear Z1, 2nd step down gear Z2 is connected by the first rotating shaft 7 with the 3rd step down gear Z3, first step down gear Z1 is meshed with the 2nd step down gear Z2 and forms first step reduction gear train 12, 3rd step down gear Z3 is meshed with the 4th step down gear Z4 being arranged on differential mechanism 1 housing and forms second stage reduction gear train 13,Differential mechanism 1 connects output shaft 3; The rotor spindle 8 of the first sun gear S1 and little motor EM1 of the first single planetary row PG1 is connected, and the 2nd sun gear S2 of the 2nd single planetary row PG2 is connected with the rotor spindle 9 of heavy motor EM2; One end of first stopper B1 is fixed on wheel box housing 10, its the other end is by the 2nd rotating shaft 11 and the first clutch coupling C0's while be connected, the other side of the first clutch coupling C0 is connected on input shaft 2, and input shaft 2 is connected with the output shaft of engine ICE by flywheel vibroshock FW; 2nd stopper B2 one end is fixed on wheel box housing 10, and its other end is connected with the rotor spindle 8 of little motor EM1; 2nd clutch coupling C1's while be connected with the rotor spindle 9 of heavy motor EM2, its other side is connected with input shaft 2; 3rd clutch coupling C2 is claw-type structure, and the 3rd clutch coupling C2 is connected with rotor spindle 8, the 2nd rotating shaft 11, first axle 5 of little motor EM1 respectively. Under the 3rd clutch coupling C2 not actuator state, the 2nd rotating shaft 11 and the first axle 5 are linked together by claw-type structure; Under the 3rd clutch coupling C2 actuator state, claw-type structure will connect the rotor spindle 8 of the 2nd rotating shaft 11 and little motor EM1. After the transmission mechanism of the present embodiment and engine link together, engine ICE, little motor EM1, sun and planet gear power coupling mechanism 4, heavy motor EM2 be arranged in co-axial alignment placement successively.
The dynamic coupling device that the present invention adopts is by the first single planetary row and the 2nd single planetary row sun and planet gear power coupling mechanism formed placed side by side, it is delivered to step down gear after the torque coupling of engine ICE, little motor EM1, heavy motor EM2 tri-propulsion source inputs, and it is delivered to wheel by differential mechanism through output shaft. Vehicle is in actual travel process, and each propulsion source combinationally uses the multiple different operating mode of generation from each shifting element (clutch coupling, stopper). It is described to the working process under the pure motorized motions of automobile and hybrid power driving below.
Under pure electric Drive Mode, this transmission mechanism can realize three kinds of operating mode, it is respectively the first gear pure electric Drive Mode EV-1, second gear position pure electric Drive Mode EV-2, the pure electric Drive Mode EV-3 in third gear position, control planning between each operating mode and shifting element is as shown in table 1, wherein representing and open state, the 3rd clutch coupling C2 corresponds to not actuator state; ● represents closed state, and the 3rd clutch coupling C2 corresponds to actuator state.
Control planning between each operating mode of table 1 transmission mechanism and shifting element
When the first stopper B1 is closed, transmission mechanism can adopt little motor EM1 or heavy motor EM2 to drive separately vehicle movement, adopts when needs high pulling torque exports heavy motor EM2, little motor EM1 to drive simultaneously, is now the first pure electric Drive Mode EV-1 of gear. The equivalent lever figure of the first pure electric Drive Mode of gear as shown in Fig. 2 (a), T in figureEM1Represent the moment of torsion of little motor EM1, TEM2Represent the moment of torsion of heavy motor EM2, TLRepresent the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represent positive moment of torsion, represent negative torque downwards, now little motor EM1 is negative rotating speed negative torque, heavy motor EM2 is the positive moment of torsion of positive rotating speed, the fulcrum balance that the first stopper B1 is provided by heavy motor, the output torque of little motor two motors and the traveling resistance of vehicle, thus maintains the in stable condition of transmission mechanism. When two motors drive simultaneously wheel can obtain drive moment of torsion be:
Twheel=[(-TEM1)*(-t1)+TEM2*(-t2+1)]*iFD
Wherein, TwheelFor the driving moment of torsion that wheel obtains;TEM1Represent the moment of torsion of little motor EM1; TEM2Represent the moment of torsion of heavy motor EM2; i1It is the first single planetary row PG1 transmitting ratio (numerical value equals the ratio of the first external toothing R1 number of teeth with the first sun gear S1 number of teeth, and this transmitting ratio is negative value); i2It is the 2nd single planetary row PG2 transmitting ratio (numerical value equals the ratio of the 2nd external toothing R2 with the 2nd sun gear S2 number of teeth, and numerical value is negative); iFDFor the reduction ratio that double reduction gearing is total.
When the 2nd stopper B2 is closed, little motor EM1 is only locked, and now transmission mechanism can only adopt heavy motor EM2 to drive, and is now the pure electric Drive Mode EV-2 in second gear position. The equivalent lever figure of the pure electric Drive Mode in second gear position as shown in Fig. 2 (b), T in figureEM2Represent the moment of torsion of heavy motor EM2, TLRepresenting the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive moment of torsion, represents negative torque downwards, and now heavy motor EM2 exports the fulcrum balance that the 2nd stopper B2 is provided by positive moment of torsion with traveling resistance. Now wheel can obtain drive moment of torsion be:
Wherein, TwheelFor the driving moment of torsion that wheel obtains; TEM2Represent the moment of torsion of heavy motor EM2; i1It is the first single planetary row PG1 transmitting ratio (numerical value equals the ratio of the first external toothing R1 number of teeth with the first sun gear S1 number of teeth, and this transmitting ratio is negative value); i2It is the 2nd single planetary row PG2 transmitting ratio (numerical value equals the ratio of the 2nd external toothing R2 with the 2nd sun gear S2 number of teeth, and numerical value is negative); iFDFor the reduction ratio that double reduction gearing is total.
When the first stopper B1, the 2nd stopper B2 and the first clutch coupling C0, the 2nd clutch coupling C1, the 3rd clutch coupling C2 are in when opening state, transmission mechanism will drive vehicle with the little motor EM1 of control and heavy motor EM2, heavy motor, little motor two motor coordination work balances travel resistance, by the stepless change of the rotating speed control realization speed of a motor vehicle to heavy motor, little motor two motors, it is now the pure electric Drive Mode EV-3 in third gear position. The equivalent lever figure of the pure electric Drive Mode in third gear position as shown in Fig. 2 (c), T in figureEM1Represent the moment of torsion of little motor EM1, TEM2Represent the moment of torsion of heavy motor EM2, TLRepresent the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represent positive moment of torsion, represent negative torque downwards, now the rotating speed size of little motor EM1, heavy motor EM2 determines the different positions of equivalent lever, so that output shaft obtains required rotating speed, it is achieved stepless change. Now wheel can obtain drive moment of torsion be:
Twheel=(TEM1+TEM2)*iFD
Wherein, TwheelFor the driving moment of torsion that wheel obtains; TEM1Represent the moment of torsion of little motor EM1; TEM2Represent the moment of torsion of heavy motor EM2; iFDFor the reduction ratio that double reduction gearing is total.
Under hybrid power driving pattern, this transmission mechanism can realize six kinds of operating mode, being respectively the first gear hybrid power drives pattern HEV-1, second gear position hybrid power to drive pattern HEV-2, third gear position hybrid power to drive pattern HEV-3, fourth gear position hybrid power to drive pattern HEV-4, fifth gear position hybrid power to drive pattern HEV-5, hybrid power reversing mode, control planning between each operating mode and shifting element is as shown in table 2, wherein representing and open state, the 3rd clutch coupling C2 corresponds to not actuator state; ● represents closed state, and the 3rd clutch coupling C2 corresponds to actuator state.
Control planning between each operating mode of table 2 transmission mechanism and shifting element
| Operating mode | B1 | B2 | C0 | C1 | C2 |
| HEV-1 | ● | 〇 | 〇 | ● | 〇 |
| HEV-2 | 〇 | ● | 〇 | ● | 〇 |
| HEV-3 | 〇 | 〇 | ● | ● | 〇 |
| HEV-4 | 〇 | 〇 | ● | 〇 | 〇 |
| HEV-5 | 〇 | ● | ● | 〇 | 〇 |
| Hybrid power reversing mode | ● | 〇 | ● | 〇 | ● |
When the first gear hybrid power drives pattern HEV-1, the 2nd clutch coupling C1 closes, and engine ICE is connected by the rotor spindle of heavy motor EM2 with sun and planet gear power coupling mechanism.Engine ICE and heavy motor EM2 drives vehicle movement just can obtain enough driving moments of torsion simultaneously, and little motor EM1 is in idle running state. First gear hybrid power drives the equivalent lever figure of pattern as shown in Fig. 3 (a), T in figureEM2Represent the moment of torsion of heavy motor EM2, TICERepresent the moment of torsion of engine ICE, TLRepresenting the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive moment of torsion, represents negative torque downwards. The driving moment of torsion that this pattern wheel can obtain is:
Twheel=(-i2+1)*iFD*(TICE+TEM2)
Wherein, TwheelFor the driving moment of torsion that wheel obtains; TICERepresent the moment of torsion of engine ICE, TEM2Represent the moment of torsion of heavy motor EM2; i2It is the 2nd single planetary row PG2 transmitting ratio (numerical value equals the ratio of the 2nd external toothing R2 with the 2nd sun gear S2 number of teeth, and numerical value is negative); iFDFor the reduction ratio that double reduction gearing is total. The sun and planet gear transmitting ratio such as selecting to commonly use and main reduction ratio, i2=-2, iFD=3.5, when engine ICE and heavy motor EM2 exports 400Nm jointly, wheel just can obtain the driving moment of torsion of 4200Nm.
When second gear position hybrid power drives pattern HEV-2, the 2nd stopper B2 closes, it is provided that the balance fulcrum of sun and planet gear power coupling mechanism, and the 2nd clutch coupling C1 closes, engine and heavy motor EM2 coaxial drive vehicle movement. The high pulling torque that this driving pattern is applicable under the higher speed of a motor vehicle exports, operating mode of such as overtaking other vehicles at a high speed. Second gear position hybrid power drives the equivalent lever figure of pattern as shown in Fig. 3 (b), T in figureEM2Represent the moment of torsion of heavy motor EM2, TICERepresent the moment of torsion of engine ICE, TLRepresenting the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive moment of torsion, represents negative torque downwards. The driving moment of torsion that this pattern wheel can obtain is:
Wherein, TwheelFor the driving moment of torsion that wheel obtains; TICERepresent the moment of torsion of engine ICE, TEM2Represent the moment of torsion of heavy motor EM2; i1It is the first single planetary row PG1 transmitting ratio (numerical value equals the ratio of the first external toothing R1 number of teeth with the first sun gear S1 number of teeth, and numerical value is negative); i2It is the 2nd single planetary row PG2 transmitting ratio (numerical value equals the ratio of the 2nd external toothing R2 with the 2nd sun gear S2 number of teeth, and numerical value is negative); iFDFor the reduction ratio that double reduction gearing is total.
When third gear position hybrid power drives pattern HEV-3, first clutch coupling C0 and the 2nd clutch coupling C1 closes simultaneously, now each element of sun and planet gear power coupling mechanism keeps same rotational speed, form direct gear, now motor rotating speed is identical with output shaft rotating speed, it is possible to obtain max. speed and heavy motor, little motor two motors can not be caused to exceed the speed range of self. Driving and adopt engine and heavy motor EM2 to drive vehicle, third gear position hybrid power drives the equivalent lever figure of pattern as shown in Fig. 3 (c), T in figureEM2Represent the moment of torsion of heavy motor EM2, TICERepresent the moment of torsion of engine ICE, TLRepresenting the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive moment of torsion, represents negative torque downwards. The driving moment of torsion that this pattern wheel can obtain is:
Twheel=(TEM2+TICE)*iFD
Wherein, TwheelFor the driving moment of torsion that wheel obtains; TICERepresent the moment of torsion of engine ICE, TEM2Represent the moment of torsion of heavy motor EM2; iFDFor the reduction ratio that double reduction gearing is total.
When fourth gear position hybrid power drives pattern HEV-4, first clutch coupling C0 closes, transmission mechanism drives vehicle movement with dynamic branch operating mode, in this mode can by the rotating speed of control little motor EM1 and heavy motor EM2, engine is made to operate in best operation interval, realizing the stepless shift function of whole car, i.e. E-CVT function, this pattern is the main hybrid electric working pattern of this transmission mechanism simultaneously.Fourth gear position hybrid power drives the equivalent lever figure of pattern as shown in Fig. 3 (d), T in figureEM1Represent the moment of torsion of little motor EM1, TEM2Represent the moment of torsion of heavy motor EM2, TICERepresent the moment of torsion of engine ICE, TLRepresenting the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive moment of torsion, represents negative torque downwards. Under dynamic branch pattern operating mode, whole car can realize stepless change, it does not have fixed drive ratio; Simultaneously each axle moment of torsion (the engine T of sun and planet gear power coupling mechanism in this operating modeICE, little motor TEM1, heavy motor TEM2, load torque TL) except the torque relationship met between each element of sun and planet gear, also want the balance of keeping system.
During the hybrid power driving pattern HEV-4 pattern of transmission mechanism employing fourth gear position, when the speed of a motor vehicle is higher, little motor EM1 rotating speed can close to zero rotating speed, cause little motor EM1 power extremely low, now the 2nd stopper B2 is closed only locks by little motor EM1, thus improving the system efficiency under this running status, this operating mode is defined as fifth gear position hybrid power and drives pattern HEV-5. Fifth gear position hybrid power drives the equivalent lever figure of pattern as shown in Fig. 3 (e), T in figureEM2Represent the moment of torsion of heavy motor EM2, TICERepresent the moment of torsion of engine ICE, TLRepresenting the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive moment of torsion, represents negative torque downwards. The driving moment of torsion that this pattern wheel can obtain is:
Wherein, TwheelFor the driving moment of torsion that wheel obtains; TICERepresent the moment of torsion of engine ICE, TEM2Represent the moment of torsion of heavy motor EM2; i1It is the first single planetary row PG1 transmitting ratio (numerical value equals the ratio of the first external toothing R1 number of teeth with the first sun gear S1 number of teeth, and numerical value is negative); i2It is the 2nd single planetary row PG2 transmitting ratio (numerical value equals the ratio of the 2nd external toothing R2 with the 2nd sun gear S2 number of teeth, and numerical value is negative); iFDFor the reduction ratio that double reduction gearing is total.
When hybrid power reversing mode, the 3rd clutch coupling C2 is in actuator state, and closed first clutch coupling C0 and the first stopper B1, is now connected to engine on the rotor spindle of little motor EM1 simultaneously. When moveing backward starting, the first clutch coupling C0 is carried out sliding wear control, now needs to be provided by C0 enough cooling oils. When reaching certain reversing speed, the rotor spindle rotating speed of little motor EM1 reaches the steady running rotating speed of engine, and the first clutch coupling C0 will be completely closed. The equivalent lever figure of hybrid power reversing mode as shown in Figure 4, T in figureICERepresent the moment of torsion of engine ICE, TLRepresenting the vehicle movement resistance being delivered on the 2nd axle, in figure, arrow represents the moment of torsion on each axle, upwards represents positive moment of torsion, represents negative torque downwards. The driving moment of torsion that this pattern wheel can obtain is:
Twheel=TECE*(-i1)*iFD
Wherein, TwheelFor the driving moment of torsion that wheel obtains; TICERepresent the moment of torsion of engine ICE; i1It is the first single planetary row PG1 transmitting ratio (numerical value equals the ratio of the first external toothing R1 number of teeth with the first sun gear S1 number of teeth, and numerical value is negative); iFDFor the reduction ratio that double reduction gearing is total.
Claims (5)
1. the transmission mechanism for forerunner's plug-in hybrid vehicle, comprise little motor (EM1), heavy motor (EM2), first clutch coupling (C0), differential mechanism, input shaft, output shaft, it is characterized in that: also comprise the first single planetary row (PG1), 2nd single planetary row (PG2), first stopper (B1), 2nd stopper (B2), first step down gear (Z1), 2nd step down gear (Z2), 3rd step down gear (Z3), described first single planetary row comprises the first sun gear (S1), the first row star-wheel (P1), the first row carrier (PC1) and the first external toothing (R1), described 2nd single planetary row (PG2) comprises the 2nd sun gear (S2), 2nd satellite gear (P2), 2nd planet carrier (PC2) and the 2nd external toothing (R2), described first single planetary row (PG1) and the 2nd single planetary row (PG2) formation sun and planet gear power coupling mechanism placed side by side, the first row carrier (PC1) of described first single planetary row is connected to form the first axle with the 2nd external toothing (R2) of described 2nd single planetary row, first external toothing (R1) of described first single planetary row is connected to form the 2nd axle with the 2nd planet carrier (PC2) of described 2nd single planetary row, 2nd axle is installed the first step down gear (Z1), 2nd step down gear (Z2) is connected by the first rotating shaft with the 3rd step down gear (Z3), described first step down gear (Z1) is meshed with the 2nd step down gear (Z2) and forms first step reduction gear train, described 3rd step down gear (Z3) is meshed with the 4th step down gear (Z4) being arranged on differential casing and forms second stage reduction gear train,Described differential mechanism connects output shaft; First sun gear (S1) of described first single planetary row is connected with the rotor spindle of described little motor (EM1), and the 2nd sun gear (S2) of described 2nd single planetary row is connected with the rotor spindle of described heavy motor (EM2); One end of first stopper (B1) is fixed on wheel box housing, its the other end by the 2nd rotating shaft and the first clutch coupling (C0) while be connected, the other side of the first clutch coupling (C0) is connected on input shaft, and input shaft is connected with the output shaft of engine by flywheel vibroshock (FW); Described 2nd stopper (B2) one end is fixed on wheel box housing, and its other end is connected with the rotor spindle of little motor (EM1).
2. a kind of transmission mechanism for forerunner's plug-in hybrid vehicle as claimed in claim 1, it is characterized in that: also comprise the 2nd clutch coupling (C1), described 2nd clutch coupling (C1) while the rotor spindle with heavy motor (EM2) is connected, its other side is connected with input shaft.
3. a kind of transmission mechanism for forerunner's plug-in hybrid vehicle as claimed in claim 1 or 2, it is characterized in that: also comprise the 3rd clutch coupling (C2), described 3rd clutch coupling (C2) is claw-type structure, and described 3rd clutch coupling (C2) is connected with the rotor spindle of described little motor (EM1), the 2nd rotating shaft, the first axle respectively.
4. a kind of transmission mechanism for forerunner's plug-in hybrid vehicle as claimed in claim 1 or 2, it is characterized in that: when the engine assembly mated mutually with performance, described engine, little motor, sun and planet gear power coupling mechanism, heavy motor be arranged in co-axial alignment placement successively.
5. a kind of transmission mechanism for forerunner's plug-in hybrid vehicle as claimed in claim 3, it is characterized in that: after the engine assembly mated mutually with performance, described engine, little motor, sun and planet gear power coupling mechanism, heavy motor be arranged in co-axial alignment placement successively.
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Address after: 528031, room 1, building 131, No. 601-604, Hua Hua Xi Road, Chancheng District, Guangdong, Foshan, China, A Applicant after: CORUN HYBRID POWER TECHNOLOGY Co.,Ltd. Address before: 410205 No. 348 west slope, Tongzi hi tech Development Zone, Hunan, Changsha Applicant before: CORUN HYBRID POWER TECHNOLOGY Co.,Ltd. |
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Effective date of registration: 20220824 Address after: No.16 Gongxin Avenue, industrial park, Yifeng County, Yichun City, Jiangxi Province Patentee after: Jiangxi Dingsheng New Material Technology Co.,Ltd. Address before: Room 601-604, Building A, Building 1#, No. 131, Jihua West Road, Chancheng District, Foshan City, Guangdong 528031 Patentee before: CORUN HYBRID POWER TECHNOLOGY Co.,Ltd. |
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